EP2348190A2 - Dampfturbinenkraftwerk - Google Patents

Dampfturbinenkraftwerk Download PDF

Info

Publication number
EP2348190A2
EP2348190A2 EP10195157A EP10195157A EP2348190A2 EP 2348190 A2 EP2348190 A2 EP 2348190A2 EP 10195157 A EP10195157 A EP 10195157A EP 10195157 A EP10195157 A EP 10195157A EP 2348190 A2 EP2348190 A2 EP 2348190A2
Authority
EP
European Patent Office
Prior art keywords
turbine
pressure
steam
thrust
thrust piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10195157A
Other languages
English (en)
French (fr)
Other versions
EP2348190B1 (de
EP2348190A3 (de
Inventor
Kristan B. Sears
Michael J. Bowman
John R. Powers
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Co
Original Assignee
General Electric Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by General Electric Co filed Critical General Electric Co
Publication of EP2348190A2 publication Critical patent/EP2348190A2/de
Publication of EP2348190A3 publication Critical patent/EP2348190A3/de
Application granted granted Critical
Publication of EP2348190B1 publication Critical patent/EP2348190B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/16—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled all the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines

Definitions

  • This present application relates generally to methods, systems, and/or apparatus for improving the operation of steam turbine engines. More specifically, but not by way of limitation, the present application relates to improved methods, systems, and/or apparatus pertaining to the operation of steam turbines with 3-flow low pressure turbines.
  • steam turbine plants may be constructed with a rotor train that, via a common shaft, connects multiple turbines that operate at varying pressure levels.
  • each of these turbines is paired with another turbine so that the axial thrust force (or "thrust") being exerted on the shaft by each may be balanced by another.
  • a steam turbine plant may include a high-pressure turbine that is paired with an intermediate-pressure turbine.
  • these turbines may be configured so that the thrust force each applies to the shaft is offset (or substantially offset) by the thrust the other applies.
  • steam turbine plants often have two low-pressure turbines that are paired with each other in the same manner, i.e., so that the thrust each applies to the shaft balances the thrust of the other.
  • the present application thus describes a steam turbine power plant that includes a first steam turbine, the steam turbine power plant including: a thrust piston operably connected to the first steam turbine via a shaft; and means for applying a supply of pressurized steam against the thrust piston such that the thrust piston applies a desired thrust force to the shaft.
  • the desired thrust force comprises a thrust force that partially balances a thrust force the first steam turbine applies to the shaft during operation.
  • the desired thrust force includes a thrust force that balances a thrust force the first steam turbine applies to the shaft during operation.
  • the desired thrust force includes a thrust force that at least partially balances a thrust force the first steam turbine applies to the shaft during operation.
  • the system may further include a second steam turbine that operates at a higher pressure than the first steam turbine; wherein the supply of pressurized steam is extracted from the second steam turbine.
  • the present application further describes a thrust piston in a steam turbine power plant that includes a rotor train including a high-pressure turbine, an intermediate-pressure turbine, and three low-pressure turbines, wherein the three low-pressure turbine include two that include a dual-flow low-pressure turbine and a single-flow low-pressure turbine; wherein the high-pressure turbine and the intermediate-pressure turbine are configured such that each substantially balances the thrust force of the other, and wherein the two low-pressure turbines of the dual-flow low-pressure turbine are configured such that each substantially balances the thrust force of the other; and wherein means for extraction supply high-pressured steam from the high-pressure turbine to a cavity disposed forward of the single-flow low-pressure turbine; and wherein the cavity, in the direction toward the single-flow low pressure turbine, is substantially bound by stationary structure that surrounds a shaft of the rotor train.
  • the thrust piston may be connected to the shaft, wherein the cavity, in the direction away from the single-flow low pressure turbine, is substantially bound the thrust piston; and wherein the thrust piston is configured to counteract a desired amount of a thrust force generated by the single-flow low-pressure turbine during operation.
  • the thrust piston is configured to counteract substantially all of the thrust force generated by the single-flow low-pressure turbine during operation.
  • a surface area of the thrust piston that bounds the cavity is configured to include a size required to counteract substantially all of the thrust force generated by the single-flow low-pressure given the pressure of the high pressure steam that is supplied to the cavity.
  • the means for extraction includes an extraction point in the high-pressure steam turbine that provides high-pressure steam to the cavity at a pressure sufficient to counteract substantially all of the thrust force generated by the single-flow low-pressure given a size of the surface area of the thrust piston that bounds the cavity.
  • the single-flow low-pressure turbine includes a position adjacent to the exhaust of the high-pressure turbine and the dual-flow low-pressure turbine includes a position adjacent to the exhaust of the intermediate pressure turbine.
  • the thrust piston includes a rigid section of the shaft that includes a larger diameter than the shaft; the thrust piston includes the cylindrical shape, the axis of which is aligned with the axis of the shaft; the thrust piston includes a relatively narrow axial thickness and a predetermined circular cross-sectional area; and the predetermined circular cross-sectional area includes a cross-section area required given the desired thrust force to counteract and the pressure level of the high-pressure steam delivered to the cavity.
  • the means for extraction includes a first conduit that is configured to extract high-pressure steam from a predetermined stage of the high-pressure turbine.
  • a second conduit is configured to direct the high-pressurized steam from the cavity to an aft stage of the high-pressure turbine, the aft stage including a stage that is downstream relative to the predetermined stage where high-pressure steam is extracted.
  • the cavity, in the direction toward the single-flow low pressure turbine is further bound by a first plurality of seals, the first plurality of seals being configured to provide a seal between the stationary structure and the shaft; and the cavity, in the direction away from the single-flow low pressure turbine, is further bound by a second plurality of seals, the second plurality of seals being configured to provide a seal between the stationary structure and the thrust piston.
  • the shaft includes a clutch that operates to desirably engage and disengaged the single-flow low-pressure turbine from the rotor train.
  • the means for extraction when the single-flow low-pressure turbine is engaged by the clutch, the means for extraction operates to supply the high-pressured steam from the high-pressure turbine to the cavity; and when the single-flow low-pressure turbine is disengaged by the clutch, the means for extraction discontinues to supply the high-pressured steam from the high-pressure turbine to the cavity.
  • Downstream and upstream are terms that indicate a direction relative to the flow of working fluid through the turbine.
  • downstream refers to a direction that generally corresponds to the direction of the flow of working fluid
  • upstream generally refers to the direction that is opposite of the direction of flow of working fluid.
  • trailing and “leading” generally refers relative position in relation to the direction of rotation for rotating parts.
  • the "leading edge” of a rotating part is the front or forward edge given the direction that the part is rotating and, the “trailing edge” of a rotating part is the aft or rearward edge given the direction that the part is rotating.
  • the term “radial” refers to movement or position perpendicular to an axis. It is often required to described parts that are at differing radial positions with regard to an axis. In this case, if a first component resides closer to the axis than a second component, it may be stated herein that the first component is “radially inward” or "inboard” of the second component.
  • first component resides further from the axis than the second component, it may be stated herein that the first component is “radially outward” or “outboard” of the second component.
  • axial refers to movement or position parallel to an axis.
  • circumferential refers to movement or position around an axis.
  • Figure 1 illustrates a schematic representation of a steam turbine power plant 100 according to a possible conventional layout.
  • the steam turbine power plant 100 may include a rotor train that includes several turbines or turbine sections, which, as stated, may be referred to given the relative pressure level of the steam that is directed through each.
  • the steam turbine power plant 100 may include a high-pressure turbine ("HP turbine”) 104, which includes a high-pressure steam feed 105, an intermediate-pressure turbine (“IP turbine”) 106, which includes an intermediate-pressure steam feed 107, and three different low-pressure turbines, two of which are part of a dual-flow low-pressure turbine (“dual flow LP turbines”) 108, which includes a low-pressure steam feed 109, and a single-flow low-pressure turbine (“single-flow LP turbine”) 110, which also includes a low-pressure steam feed 109.
  • HP turbine high-pressure turbine
  • IP turbine intermediate-pressure turbine
  • IP turbine intermediate-pressure turbine
  • three different low-pressure turbines two of which are part of a dual-flow low-pressure turbine
  • dual flow LP turbines dual-flow low-pressure turbine
  • single-flow low-pressure turbine single-flow low-pressure turbine
  • the steam turbine power plant 100 includes a steam source or boiler (not shown), which provides the supply of pressurized steam that is delivered via the steam feeds 105, 107, 109 to the turbine sections 104, 106, 108, 110.
  • a steam source or boiler not shown
  • steam supply systems may be configured to include one or more direct or indirect connections made between the boiler and the various turbine sections; or, for example, one or more connections may be made between the output or exhaust of one of the higher pressure turbine sections to the steam feed of one of the lower pressure turbine sections; or, some combination of either of those systems may be used.
  • the system may further include one or more re-heaters, pre-heaters, and/or other conventional components and systems.
  • the shaft 102 is connected to a generator 112 where the mechanical energy of the rotating shaft is converted into electricity.
  • the steam turbine power plant 100 is configured, as shown, such that the HP turbine 104 is paired with the IP turbine 106. It will be understood that the HP turbine 104 and the IP turbine 106 may be configured such that, during operation, the thrust force generated by and asserted to the shaft 102 is offset (or, at least, partially offset) by the thrust the other applies to the shaft 102. In addition, as shown in Figure 1 , the dual-flow LP turbines 108 may be paired with each other in the same manner, i.e., so that the thrust each applies to the shaft balances the thrust of the other.
  • the thrust imbalance caused by the single-flow LP turbine 110 would only need to be balanced by the thrust bearing 116 when the single-flow LP turbine 110 was engaged by the clutch 118, which likely means the costly, oversized thrust bearing 116 would only be required during peak demand periods, and rendered superfluous at all other times.
  • FIG 2 provides a schematic representation of a steam turbine power plant 200 according to another possible conventional layout.
  • the steam turbine power plant 200 includes several turbines that may be referenced given the pressure level of the steam that is directed through each, i.e., a HP turbine 104, which includes a high-pressure steam feed 105, an IP turbine 106, which includes an intermediate-pressure steam feed 107, and four LP turbines (each of which are paired in two dual-flow turbine 108 configurations), each of which includes a low-pressure steam feed 109.
  • the steam turbine power plant 200 is configured such that the HP turbine 104 is paired with the IP turbine 106 such that the thrust of each substantially balances the other.
  • the two sets of dual-flow LP turbines 108 are paired in the same manner, i.e., so that the thrust each applies to the shaft 102 balances the thrust of the other.
  • an additional single-flow LP turbine 110 (as in Figure 1 )
  • two additional LP turbines 108 are included, which, via the clutch 118, may be used to address changing load demands by engaging and disengaging the dual-flow LP turbines 108 as necessary.
  • the power plant 200 in Figure 2 is not does not allow for the same operational flexibility as the power plant of Figure 1 , as, in most applications, engaging two LP turbines 110 would overshoot the intended target and be inefficient. That is, to meet peak demands, the plant operator of Figure 2 has to activate the two additional LP turbines (i.e., the two that make up the dual-flow LP turbine 108), whereas the plant operator of Figure 1 has the option of activating a single-flow LP turbine 109. As such, in cases where only a single additional LP turbine is required, the power plant 100 of Figure 1 is much more efficient and cost-effective. As discussed above, though, the unbalanced single-flow LP turbine 110 has shortcomings of its own in that it requires a costly thrust bearing 116 to balance thrust forces.
  • FIG 3 provides a schematic representation of a steam turbine power plant 300 according to an exemplary embodiment of the present application.
  • the steam turbine power plant 300 includes the same steam turbines as those shown in the steam turbine power plant 100 of Figure 1 : a HP turbine 104, which includes a high-pressure steam feed 105, an IP turbine 106, which includes an intermediate-pressure steam feed 107, and three LP turbines 108, 110, including two dual-flow LP turbines 108 and a single-flow LP turbine 110.
  • Each of the LP turbine 108, 110 may include a low-pressure steam feed 109, as shown.
  • the HP turbine 104 is paired (and generally balanced) with the IP turbine 106, and the two dual-flow LP turbines 108 are paired (and generally balanced) with each other so that the thrust each applies to the shaft balances the thrust of the other engine.
  • the single-flow LP turbine 110 cannot be balanced by another turbine. It will be appreciated that when the single-flow LP turbine 110 is operating, it applies a considerable thrust force along the shaft 102 that must be accounted for or balanced in some way.
  • Figure 3 includes a schematic representation of the stationary turbine casing or outer structure 125 that surrounds the rotor train in that location. This depiction is provided in that section of the power plant 300 because it is particularly illustrative of the present invention. It will be appreciated that the outer structure 125 represents conventional components and structures known in the art.
  • the thrust of the single-flow LP turbine 110 is balanced or, at least, partially balanced, by a thrust piston 128 against which high-pressure steam is applied.
  • high-pressure steam acting on a thrust piston 128 that disposed in proximity to and forward of the single-flow LP turbine 110 compensates, or, at least, partially compensates, for the thrust imbalance produced by the single-flow LP turbine 110 when the single-flow LP turbine 110 is operating and engaged.
  • the thrust piston 128 may comprise a rigid section of the shaft that enlarged, i.e., has a larger diameter than the shaft 102.
  • the thrust piston 128 comprises the cylindrical shape, the axis of which is aligned with the axis of the shaft 102.
  • the cylinder generally comprises a relatively narrow axial thickness and a circular cross-sectional area that may be sized based on the particular application, as described in more detail below.
  • the thrust piston 128 generally will be constructed from conventional materials.
  • the high-pressure steam that is applied to the thrust piston 128 for this purpose may be extracted per conventional means from the HP turbine 104. From the extraction point, the supply of high-pressure steam may be directed via a first conduit 132 from the HP turbine 104 to a cavity 135.
  • the cavity 135 is a substantially enclosed space that is disposed between the thrust piston 128 and the single-flow LP turbine 110. In the direction of the single flow LP turbine 110, the cavity 135 is bound by stationary structure 125 and a plurality of seals 137 that form a seal between the stationary structure 125 and the shaft 102.
  • the seals 137 may comprise conventional seals that operate to provide a seal between stationary components, which in this case is the stationary structure 125, and rotating components, which in this case is the shaft 102.
  • the seals 137 may be brush seals, hi-lo seals, or other types of seals.
  • the cavity 135 may be adjacent to and bound by the thrust piston 128 and seals 137 that form a seal between the stationary structure 125 and the thrust piston 128.
  • the seals 137 may comprise conventional seals that operate to provide a seal between stationary components, which in this case is the stationary structure 125, and rotating components, which in this case is the outer radial edge of the cylindrical thrust piston 128.
  • a second conduit 141 returns the pressurized steam from the cavity 135 to the downstream stages of the HP turbine 104. Thereby returned, the steam may be exhausted into the later stages of the HP turbine 104.
  • This configuration may limit the loss of steam to the system.
  • the steam from cavity 135 may be used for other purposes also. For example, it may be supplied to the IP turbine or one of the LP turbines, or used in a heating system.
  • a clutch 118 may be provided so that the single-flow LP turbine 110 may be engaged when needed and disengaged when load demands are adequately satisfied by the other available turbines of the power plant 300.
  • the single-flow LP turbine 110 is disengaged, it will be appreciated there is no net thrust to balance.
  • the high-pressure steam supply from the HP turbine 104 may be shut-off, which makes the steam that would have been extracted available to the HP turbine 104.
  • the shut-off of the high-pressure steam may be done via a valve 143 or other conventional methods.
  • the thrust piston 128 required to balance the single-flow LP turbine 110 may remain relatively compact in size. More particularly, it will be understood that the size of the thrust piston 128 that is required to balance the single-flow LP turbine 110 is dependent upon the pressure of the steam that is supplied to the cavity 135. A lower-pressure supply of steam requires a thrust piston 128 having considerable surface area against which the steam may exert its force.
  • a higher-pressure supply of steam requires less surface area against which to push, while still balancing the thrust force of the single-flow LP turbine 110.
  • the extraction of the steam from the HP turbine 104 provides the high-pressure supply of steam that allows a relatively small, cost-effective thrust piston 128 to balance the single-flow LP turbine 110.
  • a known, convenient extraction point within the HP turbine 104 may available and the thrust piston 128 designed to accommodate that particular extraction point. That is, given the pressure of the steam that may be provided to the cavity 135 from the extraction point and the thrust force of the single-flow LP turbine 110 for which compensation is required, the thrust piston 128 may be designed so that necessary surface area is available.
  • the thrust piston 128 may be designed based on other criteria or limitations and the steam extraction point determined based on it. That is, given the thrust force for which compensation is required and the surface area of the thrust piston 128, an extraction location within the HP turbine 104 may be determined which provides steam at the desired pressure to the cavity 135.
  • the thrust piston 128 also may be configured so that it balances only a portion of the thrust force created by the single-flow LP turbine 110.
  • the thrust piston 128 may be configured to partially balance the thrust of the single-flow LP turbine 110 while thrust bearings 116 are included to provide balance to the system. In these cases, it will be appreciated that the size of the thrust bearings 116 likely would be much reduced, which may make this an attractive alternative in certain applications.
  • the single-flow LP turbine 110 may be connected to the shaft 102 adjacent to or near the exhaust of the HP turbine 104, while the dual-flow LP section is connected to the rotor train adjacent to the exhaust of the IP turbine 106, as depicted in Figure 3 .
  • this application is exemplary only. It will be appreciated that the same principles may be used to balance the thrust of turbines in other types of power plant configurations.
  • the principles provided herein may be used effectively to provide balance to any steam turbine (low pressure or otherwise) in a system that includes a steam turbine that operates at a higher pressure or has another supply of higher pressured steam.
  • steam may be extracted from the HP turbine 104 and directed via the conduit 132 to the cavity 135.
  • the pressurized steam asserts an axially aligned force in both directions.
  • the steam In the direction toward the single-flow LP turbine 110, the steam primarily presses against the stationary structure 125. (A small portion of the steam presses against the seal 137 and a smaller portion escapes through the seals 137.
  • the system is configured such that the steam that escapes through the seals 137 enters the single-flow LP turbine 110 where it may be used.)
  • the steam within the cavity 135 presses primarily on the thrust piston 128.
  • the net effect of the pressure with the cavity 135 is a thrust force being applied on the shaft 102 away from the single-flow LP turbine 110.
  • the size of this net force may be configured by varying the surface area of the thrust piston 128 so that a desired portion of the thrust force created by the single-flow LP 110 turbine is counteracted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
EP10195157.2A 2009-12-31 2010-12-15 Dampfturbinenkraftwerk Active EP2348190B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US12/650,848 US8425180B2 (en) 2009-12-31 2009-12-31 Systems and apparatus relating to steam turbine operation

Publications (3)

Publication Number Publication Date
EP2348190A2 true EP2348190A2 (de) 2011-07-27
EP2348190A3 EP2348190A3 (de) 2017-11-08
EP2348190B1 EP2348190B1 (de) 2019-04-03

Family

ID=44065689

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10195157.2A Active EP2348190B1 (de) 2009-12-31 2010-12-15 Dampfturbinenkraftwerk

Country Status (4)

Country Link
US (1) US8425180B2 (de)
EP (1) EP2348190B1 (de)
JP (1) JP2011137449A (de)
RU (1) RU2554161C2 (de)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI432523B (zh) 2011-06-21 2014-04-01 Asahi Kasei E Materials Corp And an inorganic composition for transfer of fine asperity structure
JP6652662B2 (ja) * 2016-12-12 2020-02-26 東芝エネルギーシステムズ株式会社 タービン及びタービンシステム
JP7093238B2 (ja) * 2018-06-18 2022-06-29 三菱重工業株式会社 蒸気タービン設備及びコンバインドサイクルプラント
JP7134002B2 (ja) * 2018-07-04 2022-09-09 三菱重工業株式会社 蒸気タービン設備及びコンバインドサイクルプラント
CN113047911B (zh) * 2021-03-10 2022-01-14 东方电气集团东方汽轮机有限公司 一种推力平衡结构
US11486370B2 (en) 2021-04-02 2022-11-01 Ice Thermal Harvesting, Llc Modular mobile heat generation unit for generation of geothermal power in organic Rankine cycle operations
US11359576B1 (en) 2021-04-02 2022-06-14 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11480074B1 (en) 2021-04-02 2022-10-25 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11421663B1 (en) 2021-04-02 2022-08-23 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power in an organic Rankine cycle operation
US11493029B2 (en) 2021-04-02 2022-11-08 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11644015B2 (en) 2021-04-02 2023-05-09 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11255315B1 (en) 2021-04-02 2022-02-22 Ice Thermal Harvesting, Llc Controller for controlling generation of geothermal power in an organic Rankine cycle operation during hydrocarbon production
US11592009B2 (en) 2021-04-02 2023-02-28 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US12312981B2 (en) 2021-04-02 2025-05-27 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11293414B1 (en) 2021-04-02 2022-04-05 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power in an organic rankine cycle operation
CN114991894B (zh) * 2022-04-27 2023-07-04 东方电气集团东方汽轮机有限公司 有限容积工质全运行段高负荷率的透平系统及运行方法
US12534990B2 (en) 2022-12-29 2026-01-27 Ice Thermal Harvesting, Llc Power generation assemblies for hydraulic fracturing systems and methods
US12180861B1 (en) 2022-12-30 2024-12-31 Ice Thermal Harvesting, Llc Systems and methods to utilize heat carriers in conversion of thermal energy
US11852039B1 (en) * 2023-03-16 2023-12-26 Elliott Company Steam turbine with redundant low pressure section

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2300758A (en) * 1941-05-13 1942-11-03 Westinghouse Electric & Mfg Co Blading and balancing piston arrangement
GB1105658A (en) * 1964-07-22 1968-03-13 Ass Elect Ind Improvements in or relating to turbines
US3614255A (en) * 1969-11-13 1971-10-19 Gen Electric Thrust balancing arrangement for steam turbine
JPS589543A (ja) * 1981-07-07 1983-01-19 Toshiba Corp 蒸気タ−ビン発電装置
JPS63195303A (ja) * 1987-02-09 1988-08-12 Toshiba Corp 蒸気タ−ビン発電装置
JPH02196101A (ja) * 1989-01-25 1990-08-02 Fuji Electric Co Ltd 蒸気タービンのスラスト低減装置
US4961310A (en) * 1989-07-03 1990-10-09 General Electric Company Single shaft combined cycle turbine
JPH05156902A (ja) * 1991-12-03 1993-06-22 Mitsubishi Heavy Ind Ltd タービンのスラスト調整装置及び方法
JP3529412B2 (ja) * 1993-12-09 2004-05-24 株式会社東芝 一軸型コンバインドサイクルプラント
FR2719627B1 (fr) * 1994-05-03 1996-06-14 Gec Alsthom Electromec Unité de production d'énergie électrique à cycle combiné comportant une turbine à gaz et une turbine à vapeur à plusieurs modules.
JPH08177409A (ja) * 1994-12-27 1996-07-09 Toshiba Corp 蒸気タービンプラント
DE19953123A1 (de) * 1999-11-04 2001-05-10 Abb Alstom Power Ch Ag Schubausgleich einer Turbogruppe
EP1445429A1 (de) * 2003-02-07 2004-08-11 Elsam Engineering A/S Dampfturbinensystem
US7195443B2 (en) * 2004-12-27 2007-03-27 General Electric Company Variable pressure-controlled cooling scheme and thrust control arrangements for a steam turbine
EP1780376A1 (de) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Dampfturbine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Also Published As

Publication number Publication date
EP2348190B1 (de) 2019-04-03
US20110158790A1 (en) 2011-06-30
RU2554161C2 (ru) 2015-06-27
EP2348190A3 (de) 2017-11-08
JP2011137449A (ja) 2011-07-14
US8425180B2 (en) 2013-04-23
RU2010153540A (ru) 2012-07-10

Similar Documents

Publication Publication Date Title
EP2348190B1 (de) Dampfturbinenkraftwerk
EP3763931A1 (de) Elektrischer generator eines gasturbinentriebwerks
US9574500B2 (en) Direct metering using a variable displacement vane pump
US7112036B2 (en) Rotor and bearing system for a turbomachine
US20090211260A1 (en) Multi-Spool Intercooled Recuperated Gas Turbine
EP3269964B1 (de) Gasturbinenmotor ein getriebe umfassend
US20170298830A1 (en) Oil-free gas turbine engine
US20190293117A1 (en) Closed Cycle Heat Engine
JP6881887B2 (ja) 単一型低損失軸受及び低密度材料を有する機械駆動構成
JPH0658043B2 (ja) 蒸気注入式ガスタービンエンジンとその運転方法
JP2016041935A (ja) モノタイプの低損失軸受および低密度材料を備えるパワートレインアーキテクチャー
JP2016041930A (ja) ハイブリッドタイプの低損失軸受および低密度材料を備えるパワートレインアーキテクチャー
JP2016041936A (ja) ハイブリッド型低損失軸受及び低密度材料を有する機械駆動構成
CN109854378A (zh) 一种具有模式调节能力的涡轮风扇发动机
CA2786040C (en) Gas turbine engine and high speed rolling element bearing system
EP2422049B2 (de) Verbesserte turbine für die expansion von gas/dampf
CN103688022B (zh) 用于运行旋转机械的方法
US11203934B2 (en) Gas turbine engine with separable shaft and seal assembly
EP2341228B1 (de) Turbomaschine mit miteinander gekuppelten Turbinenrädern
EP3056695B1 (de) Wellenanordnung eines einwellen-kombikraftwerks
Brun et al. A novel centrifugal flow gas turbine design

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F01D 3/02 20060101AFI20171002BHEP

Ipc: F01D 3/04 20060101ALI20171002BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180508

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20181217

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1115973

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190415

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602010057963

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190403

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1115973

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190703

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190803

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190704

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190703

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190803

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602010057963

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

26N No opposition filed

Effective date: 20200106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20191231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191215

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191215

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191231

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191231

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191231

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20201123

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20101215

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190403

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20211215

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211215

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602010057963

Country of ref document: DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 602010057963

Country of ref document: DE

Owner name: GENERAL ELECTRIC TECHNOLOGY GMBH, CH

Free format text: FORMER OWNER: GENERAL ELECTRIC COMPANY, SCHENECTADY, N.Y., US

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20251126

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20251120

Year of fee payment: 16